Landing gear



Jan. 3, 1939.A u c. G. sEYr-'ERTH LANDING GEAR Filed May l5, l9m36 4 Sheets-Sheet l y BY x-;

NQ mm. Nm. N0..

Jan. 3, 1939-. c. G. sEYFERTH LANDING GEAR Filed May 13, 1956. 4 Sheets-Sheet 24 ATTORNEYS.

Jan. 3, 1939.

` LANDING GEAR Filed May 15, 1956 4 Sheets-Sheet 5 l' v"Illv y v(cz/G. sEYFl-:RTH 2,142,216

Jan. 3, 1939. as. sEYFr-:RTH

LAND I NG' GEAR Filed Mayl, 1936 4 Sheets-SheefI 4 Patented 3, 1939 UNITED STATES TENr erica LANDING vGEILE Carl G. Seyfcrth, Muskegon, Mich. Application May 13, 1936, Serial No. 79,540

4 Claims. (Cl. 28B- 331) This invention relates in general to landing gears, and has more particular reference to retractible landing gears for semi-trailers and the like.

5 A principal object of the invention is the provision of a novel hydraulic landing gear employing double acting rams. y

An important object of the invention is the provision of an hydraulic landing gear for a trailer vehicle which is automatically operated during coupling and uncoupling of the trailer and its tractor.

Another important object of the invention is theprovision in such an hydraulic landing gear o f a novel adjustable wheel truck or assemblage.

A further important object of the invention is the provision of automatically operable means for locking the landing gear in retracted position.

Another important object of the invention is the provision in such an hydraulic landing gear of a horizontal brace which also functions as a protective housing for certain of the uid conduits.

Numerous other objects and advantages of the invention will be apparent as it is better understood, from the following description, which, when taken in connection with the accompanying drawings, discloses a preferred embodiment thereof.

In the drawings,

Figure 1 is a top plan view of the chassis`of a part of a trailer provided with a landing gear embodying the features of the invention;

Fig. 2 is a longitudinal'section taken substantially on line 2-2 in Fig. 1;

Fig. 3 is a vertical sectional view of one of the hydraulic rams employed;

Fig. 4 is a detail elevational view of a, part of the landing gear, illustrating the hinged arrangement;

Fig.-5 is a front elevational view, partly in section, of a part of a trailer provided with a modied form of hydraulic landing gear which is adapted to be manually controlled and operated;

Fig. 6 is a longitudinal section through one of the hydraulic rams of Fig. 5;

Fig. 'I is a detail planview of the device of Figa 6; Y

Fig. 8 is a side elevational view of the mechanism of Fig. 5 with parts shown in section;

Fig. 9 is a detail rear elevational view part of the landing gear of Fig. 5;

Fig. 10 is an enlargedplan view of the pump and control mechanism therefor of Fig. 5, and

ofa

` u Fig.. 11 is an enlarged detail plan View lo: a

part oi the hydraulic system, showing the check valves in horizontal section.

Referring more particularly to the drawings, reference numeral Il indicates in general a. trailer or a semi-trailer vehicle having side frame 5 members I2, and being provided adjacent its forward end with a retractible landing gear embody-v ing the features of the instant invention and designated generally by reference numeral I3.

The landing gear I3 is\of the swinging type, 10 and comprises a pair of hinged supporting members indicated generally at i4, and a movable wheel carrying structure associated with each supporting member I4 and indicated generally by reference numeral I5. In the retracted position 15 of the landing gear I3, the wheel carrying structures I5 are moved upwardly and rearwardly to their full line position of Fig. 2, while in extended position, as shown in dotted lines, the landing gear I3 is adapted to support the forward end of 20 the trailer.

Each supporting member I4 comprises a substantially cylindrical shaft I6 whch is adapted to be hingedly connected at il to asupporting' bracket I8 (Fig. 4). are `fastened to the side frame members I2 by means of rivets or the like I9. Each bracket I8 has formed integrally therewith an overhanging member or stop 2| to limit forward movement o the supporting member I4.

'Ihe wheel carrying structures i5 are slidably mounted upon the cylindrical shafts I6 and comprise casings 22, bolts 23 and wheels 24. 'I'he casing 22 is adapted to be moved upon the shaft I 6 so as to provide a means for 'raising or lowering 35 the wheels 24 relative to the shaft toinsure proper adjustment thereof. The wheels 24 are rotatably mounted upon a cross shaft 25, the shaft 25 being held in place in the casings 22 by. means of the usual clamping members 26.

A forked or radiusrod 211s pivotally mounted at its spaced ends upon a cross shaft 28, which is in turn connected at its ends to the shafts I6, and

the converging end of the rod'Z'I is pivotally mounted at 29 upon a depending arm 3| whichis 46 integral with a double acting ram indicated generally by the reference numeral 32, the operation of which will be more fully described hereafter. The stationary end of the double acting ram 32 is secured to a cross frame member 33 by means 5o of a pin 34 engaging a suitableaperture 35 (Fig. 3) in an iextension 36 of a cap 31 of .the ram structure 32, the extension 36 being disposed between parallel brackets 38 secured to the frame member 33. 5.5

The supporting brackets I8 25 Referring more particularly to Fig. 3, the cap 31 of the ram structure 32 is provided with a suitable port 39 which may be threaded adjacent its outer end with a standard pipe thread tap, and has an internally threaded skirt portion 4| adaptedto'be screwed onto the forward end of a tube or hollow cylinder 42.

A plug member 43 is screwed into the other end of the tube 42, and is provided with an axial bore 44 through which a shaft or piston 45 extends, and a right angled passage-way or port 46 which is threaded adjacent its outer end, similarly to the port 39, and communicates with the interior of the cylinder 42 at its inner end. The rearward end of the bore 44 is enlarged to provide space for suitable packing 41 which is held in place by means of a nut or thimble 48 screwed into the enlarged part of the bore 44.

The forward end of the piston rod 45 is reduced, as indicated at 49, and this reduced portion is threaded at its extreme end. A compound piston is mounted on the reduced portion 49, comprislnga washer 5| abutting against the shoulder at the bottom of the reduced portion, a leather cup 52 inverted over the washer 5|, a ring 53 abutting against the leather cup 52 and constituting the main part of the piston, a second.

leather cup 54 similar to the cup 52`but reversed with respect thereto, and a washer 55 disposed within the cup 54. These several members that are mounted on the reduced portion 49 of the piston rod 45 are rigidly secured thereto by meansy of a nut 56.

The rear end of the rod 45 is reduced, as indicated at 51, and this reduced portion is threaded at its extreme end. A plug 58 is mounted on the reduced portion 51 and has its outer surface threaded so as to fit the threads on the inner surface of a casing or tube 59. The plug 56 is held in place upon the reduced portion 51 by means of a nut 6|. The casing 59 is adapted to engage and slide upon a casing 62 which is fitted over the cap 31 and the plug 43`so that there is a continuous surface upon which the casing 59 may slide. The bracket 3| ls also an integral part of the casing 59 so that any movement that may be imparted to the casing is in turn transmitted to the bracket 3| and the rods 21. A bracket 53 is fastened in any suitable manner to a cross frame member 64, and slidably engages the casing 59 to hold the hydraulic ram in position and permit free longitudinal movement of the casing.

A second double acting hydraulic ram, generally indicated by the reference numeral 65 yis fastened forward of the hydraulic ram 32, the construction of the hydraulic ram 65 being similar to that of the ram 32. One end of the hydraulic ram 65 is fastened to a bracketv 66 which is secured to a cross frame member 61. A rod 68, similar to the rod 45,is held in position by means of a pin 69, said pin passing through the rod 68 and a pair of laterally extending ears 1| formed integrally with the bracket 66. The other end of the rod 68 is reduced, as indicated at 12, and this reduced portion is threaded at its forward end.

A sliding plate 13 is fastened to the reduced portion 12 by means of a nut 14. Pivotally mounted upon the sliding plate 13 at 15 are a pair of movable jaw members 16. The jaw members 16 are adapted toy engage a king pin 11, which constitutes part of the tractor, in the usual and well-known manner. 'Ihe jaw members are held in closed or king pin engaging position by-a pair of longitudinally extending guides 18, which flare outwardly at their forward end 8| comprises a lever 82 which is pivotally mounted at 83 upon a bracket member 84 secured to the trailer frame. A bell crank member 85 is also pivotally mounted at 83, and is provided on one arm thereof with a stop or lug 86 for engagement with the lever 82. The other arm 81 of the bell crank 85 has one end of a rod 88 pivotally mounted upon it, which rod is in turn pivotally mounted upon one arm of a bell crank 89. The bell crank 89 is pivotally mounted at 9| upon a stationary guide plate 92. The other arm 93 of the bell crank 89 is fastened to an emergency brake rod 94 which in turn is fastened to the brake 'drums of the wheels of the trailer (not shown).

One end of a link 95 is also pivotally secured to the inner end of the rod 88, and its other end is pivotally connected to the outer eno of a bell crank lever 96. The lever 96 has a pin and slot connection at 91 intermediate its ends with the stationary guide plate 92, and terminates at its inner end in a cam projection 98. The inner end of the rod 88 is` also secured to a sliding locking bolt 99 which is adapted to engage within a suitable recess in the sliding jaw carrying plate 13 (Fig. 2). The toggle mechanism 8| is similar to that disclosed in U. S. Letters Patent No. 2,028,400, issued January 21, 1936, to C. H. Land et al. and its operationwill be described hereinafter.

The hydraulic ram 65 is adapted to actuate the hydraulic ram 32. A tube |02 connects the hydraulic ram 65 at its forward end to the hydraulic'ram 32 at the port opening 46. Another tube |03 connects the rearward end of the hydraulic ram 65 with the hydraulic ram 32 at the port opening 39. The tube |02 has an auxiliary -tube |04 which is connected to a reserve tank |05. A check valve is placed in the auxiliary line |04 to allow the flow of iluid to be in one direction only. A second auxiliary tube |01 is inserted in the line |03, and is provided with a check valve |08 which permits the flow of fluid in one direction only. A vent |09 is inserted in the reserve tank |05 to allow the tank to be open to the atmosphere. The purpose of the tank |05 Fig. l. Such movement of the lever 82 swings the bell crank 85 in a counterclockwise direction "(Fig, l) to set the toggle mechanism 8| in the manner more specifically described in my copending application. 'Briefly, this results in an outward movement of the rod 88 against the pressure of the spring surrounding the same to set the parking brake through the agency of the -lever 89V and rod 94, straightenthe toggle linkage 95, 96, and pull the bolt 99 outwardly from the recess |0| in the sliding guide plate 13. The toggle. mechanism will remain in this set position,

'Ihe operator, having thus set the toggle mechanism and released the sliding plate 13 fromI the locking bolt 93, has merely to drive the tractor away from the trailer, the parking brakes maintaining the trailer stationary. As the tractor is driven forward, the king pin 11 forming a part of the usual fth wheel mechanism mounted thereon will pull the jaws 16 and plate 13 forward relative to the trailer. The guides 10 will maintain the jaw members 16 in king pin engaging position until the jaws reach the flared portion 19 of the guides. At this point the king pin '11 will spread the jaw members 16 apart and disengage'itself therefrom to complete the disconnection of the tractor from the trailer.A

In this forward ,movement of the sliding plate 13, the piston rod 68 of the hydraulic ram 65 is pulled forwardly to force the liquid in the forward part of the ram through the conduit |02 and port 46 into the rear part of thehydraulic ram 32. This will force the piston of the ram 32 andthe piston rod 45 forward, during which movement, the liquid in the forward part of the ram 32 will be forced out through the port 32 and conduit |03 into the rear end of the ram 65. Since the piston in the ram 65 is moving forward at this time,

a low pressure will be created in the rear portion of the ram to aid in this movement of the liquid from the ram 32 to the ram 65. This low pressure in the rearward portion of the ram 65 will f also insure sufilcient liquid being carried therein through the check valve |08 and conduit |01 from the reserve tank |05, if there \be a deficiency of liquid in the system due to leakage, or the like. It will be understood that the capacity of the ram 65 when the piston rod 60A is in its rearward position of Figs. l and 2 is equal to the capacity of the ram 32 when the piston rod 45 is at the end of its forward stroke, and the capacities of the two rams 65 and 32 are also equal when the piston rod 68 is in its forward position and the piston rod 45 is in its rearward position of Figs. 1 and 2.

The forward movement of the piston and the piston rod 45 of the rear hydraulic ram 32 pulls the sleeve 59 and the arm 3| forward to lower the landing gear I3 through the agency of the rod 21 into its dotted line position of Fig. 2. Such movement of the landing gear to its lowered position will necessarily take place before the king pin 11 has disengaged itself from the jaw members 16 and while the trailer is still supported by the tractor, since the distance of travel of the king pin with the jaws 'I6 which is enforced by the guides 18 is equal to the maximum longitudinal movement of the piston rod 68 of the forward hydraulic ram 65. y

When it is desiredto recouple the tractor with the trailer, all that is necessary is to back the former rearwardly` into engagement with the In this movement, the king pin 1;1 willv latter. engage the jaw members 16, since the latter will remain in their forward open position, and will push them, together with the sliding plate 13, rearwardly relatively to the trailer. As the sliding plate 13 reaches its rearward position of Figs. 1 and 2, it will engage thel cam end portion-98 of the toggle lever 96 to trip the toggle mechanism and allow the spring surrounding the rod 88 to return the same to its position of Fig. 1. Inthis return movement, the locking bolt 93 is moved into the recess |0| of the sliding plate 13 to lock the latter and the jaw lmember 16 in their final position of Fig. 1. The bell crank 89 is also swung back to its position of Fig. 1 to move the rod 94r forwardly to release the parking brakes. 'Ihe rearward movement of the sliding plate 13 5 relative tothe trailer will push the piston rod 68 and piston of the forward hydraulic ram 65 rearwardly. This will force the liquid within the ram 65 through the conduit |03 and port 39 into the forward portion of the rear hydraulic ram 32 10 to move the piston and piston rod 45 of the latter rearwardly and force the liquid therein through the conduit |02 into the forward end of the hydraulic ram 65. If there be a deficiency of liquid in this portion of the system, it will be made 15 up by liquid from the reserve tank |05 being drawn through the check valve |06 and auxiliary conduit 04,' due to the low pressure created in the forward portion ofthe ram 65. Such rearward movement of the piston rod 45 of the hydraulic 20 ram 32 will slide the sleeve 59 and rod 3| rearwardly to raise the landing gear |3 to its full line position of Fig. 2,

It will be readily apparent that in the forward movement of the piston in the hydraulic ram 65,` 25 as the liquid is forced therefrom through the cond'uit |02,'the check valve |06 will prevent any flow of this liquid from the conduit |02 into the reserve tank |05. Similarly,.in the forward movement of the piston inthe hydraulic ram 32 to force the 30 liquid through the conduit 03, the check valve |08 will prevent any of this liquid from being forced into the reserve tank |05. However, if at any time there is a deficiency of liquid in the system, the low pressure created in that portion of 35 the particular hydraulic ram 32 or -65 from which its associated piston is being moved, will cause additional liquid to ilow from the reserve tank |05 into that portion of the particular hydraulic ram, through either the valve |06 or i the valve |00, 40 depending upon which of the conduits |02 or |03 is connected to the low pressure side of the particular hydraulic ram. This automatic addition of sufficient liquid from the reserve tank |05 to the affected part of the hydraulic system is aided by 45 the mounting of the, tank |05 at the highest point of the system (as seen in Fig. 2), which provides an additional pressure head at this point.

It will also be' clearly apparent that any air whichmay become entrained within any portion of the hydraulic system will be collected in the conduit |04 and/or the conduit |01, which conduits are alternately under a low pressure during alternate raising and lowering operations of the instant landing gear. So long` 'as'there is a fulll supply of liquid in the hydraulic system, there will normally be no air entrained therein, but any air which may be in the system will be collected in the conduits `|04 and |01, as above described. Consequently, when either the check valve |06 or the 60 check valve |08 is opened, due to the flow of vliquid from the reserve tank 05 into the system in the`v automatic addition of liquid to compensate for p loss by leakage, the air entrained in the system which has collected in the associated conduits |04, |01. will be allowed to escapeupwardly therefrom into the reserve tank |05. This escape action of the air entrained within the hydraulic system is facilitated by the provision of tlievent |09 on the' reserve tank |05, which is open to the atmosphere.

Referring to'Figs. 5 to l0, a modified form of hydraulic landing gear is shown which is of the i and a movable wheel carrying structure associated with each supporting member ||4 and designated generally by reference numeral `I l5. In the retracted position of the landing gear ||3, the wheel carrying structures ||5 are telescoped linto their respective supporting members ||4, the wheels assuming their upper broken line position of Fig. 8, while in extended position, as shown in full lines in Figs. 5 and 8, the landing gear is adapted to support the forward end of the trailer. l

Each supporting member |I4 comprises a hollow, substantially cylindrical housing ||6 which is formed integral with a vertically disposed backing plate ||1 and a supporting bracket ||8 on its inner side (Figs. 5 and 8). 'Ihe supporting surfaces of the brackets II8 are curved or otherwise shaped to t the lower surface of the side frames I I2 of the trailer II |,-'and, together with the plates |I1, are rigidly secured to said trailer frame members I|2 in any suitable manner.

Adjacent their low'er ends, each of the supporting members II4 is provided with a hollow, inwardly directed, horizontally disposed extension I|9 formed integral with the housing |I6.

` Extending into and rigidly secured at each end in any desired manner to these extensions ||9 is a horizontally disposed tubular brace |2| for imparting rigidity and stability to the landing gear structure.

Adjacent their upperends, each of the supporting members ||4 is provided with a pair of spaced, parallel brackets |22 formed integral with the backing plate I|1 and extending outwardly therefrom over the open upper end of the housing |I6. A horizontally disposed pin |23 is mounted in each pair of brackets |22 in alinement with the axis of the related housing I |6.

The upper end of a double acting hydraulic ram structure, indicated generally by reference numeral |24, is secured to each of the supporting members ||4 by means of the pin |23 engaging a suitable aperture |25 (Figs. 6 and 7) 1n an extension |26 of a cap |21 of the ram structure |24, the extension |26 being disposed between the parallel brackets |22.

Referring more particularly to Fig. 6, the cap |21 of the ram structure |24 is provided with a suitable port |28 which may be threaded adjacent its outer end with a standard pipe thread tap, and has an internally threaded skirt portion |29 adapted to be screwed onto the upper end of a tube or hollow cylinder |3I.

A plug member |32 is screwed into the lower end of the tube |3I, and is provided with an axial bore |33 through which a, shaft or piston rod |34 extends, and a right angled passageway .or port |35 which is threaded adjacent its outer as indicated at |38, and this reduced portion is threaded at its extremev end. A compound plston is mounted on the reduced portion |38, comprising a washer |39 abutting against the shoulder at the bottom o! the reduced portion, a leather cup I4| inverted over the washer |38, a ring |42 on top of the leather cup |4| constituting the main part of the piston, a second leather cup |43 similar to cup |4| but inverted with respect thereto, and a washer |44 disposed within the cup |43. These sever'al members that are mounted on the reduced portion |38 of the piston rod |34 are rigidly secured thereto by means of a nut |45.

The above described hydraulic ram structure |24 is operable by means of a pump unit |48 oi.' well-known construction (Figs. 5 and 8) which includes a pump and iiuid reservoir and is rigidly mounted on the trailer frame in any suitable manner. as by means ofv a. bracket |41, which maybe secured thereto or formed integral with one of the supporting members ||4. The pumpunit |46 comprises an operating handle or lever |48 which is preferably removably secured to a s'haft |49 (Fig. 10) by being threaded into a suitable tapped aperture therein. Rigidly Isecured to the shaft |48 is a rocker arm |5|, each of the ends of which is pivotally secured to a. piston rod |52 of a pump of usual construction.

By oscillating the handle |48, the piston rods |52 will bev alternately operated to force fluid from a reservoir |53, constituting part of the pump unit |46, through one or the other of a pair of uid conduits |54, |55. A valve handle |56 in the form of a removable socket wrench constitutes a manual control for selectively determining the direction of iiow of the liquid, that is, for controlling the operation of the pump to force liquid from the pump unit through the conduit |54 or through the conduit |55.'

The conduit |54 is connected in any suitable manner to two conduits |51 and |58 which are connected at their other ends to the upper ports |28 of the two hydraulic ram structures |24, respectively. The conduit |55 is similarly connected to two conduits |59 and |6I which in turn are connected at their other ends to the lower ports |35 of the two hydraulic ram structures |24, respectively. The two conduits |58 and I6| leadingr to the ram structure |24 on the far side of the vehicle from. the pump and reservoir unit |46 (Fig. 5) are housed within the tubular brace |2| for protection, having access thereto through suitable apertures |62 in the rear surface of the tubular extensions IIS.

'I'he' lower end of each piston rod |34 of the 'hydraulic ram structures |24 is provided with a horizontal aperture |63 (Fig. 6) through which a retaining bolt |64 (Figs. 5 and 8) is inserted.

The bolt |64 also extends through suitable apertures inthe side walls of a thrust bearing member I65'and a tubular housing |66. The housing |66 comprises a part of the wheel carrying structure ||5, and is'of such external diameter as to t slidingly into the cylindrical housing ||6 of the supporting member ||4.

'I'he upper part of the thrust bearing member.

|65 is substantially cylindrical in shape, so as to fit into the lower end of the tubular housing |66, and terminatesin a horizontal shoulder |61 upon which the bottom end of the housing |66 rests. The upper part of the thrust bearing member |65 is also provided with a vertical, centrally located, cylindrical recess or bore |68 into which the lower end of the piston rod |24 extends. The rod |34 abuts against the bottom of the recess |68 so that very little strain is thrown on the retaining son |64.

'I'he lower part of the thrust bearing member |65 is provided with a horizontally disposed bore |69 (Fig. 8) through whicha removable bearing pin |1| extends. A semi-cylindrical recess |12 is provided through the bearing member |65- at the bottom of and crosswise to the bore |69, and a complementary groove is provided in the bearing pin which, together with the recessY |12, comprises a recess through which `a retaining bolt |13 extends for preventing displacement of the bearing pin |1|.

A circular yoke member or wheel truck |14 is provided with a pair of vertically spaced, horizontally disposed apertures |15 and |16 extend* ing through b'oth side portions thereof parallel with the longitudinal axis of the trailer vehicle The thrust bearing member |65 extends downwardly into the wheel truck' |14 and the bearing pin |1| is adapted to be seated in either pair of apertures |15 or |16 (Fig. 8).

Formed integral with the circular yoke member or wheel truck |14 on each side thereof (Fig. 5,) is one of a pair of trunnions |11. Rotatably mounted on each trunnion |11 is a wheel |18, the

axial movements of which are limited by a shoullder on the trunnion and a removable cap |19 which is retained on the end of the trunnion by means of a bolt |8|.

With the above described arrangement, the wheels |18 and wheel truck |14 Yare pivotally mounted for limited movement laterally of the vehicle on the bearing pin |1|. In order to resiliently maintain the wheels in their 'vertical position, al pair of upwardly extending leaf springs |82 are mounted on each'side of the thrust bearing member |65, between the latter and the inside surface of the wheel truck |14. These springs |82 are shaped to substantially conform to the inner surface of the wheel truck |14 with their upper ends free and bearing against said wheel truck and their lower ends retained by the bolt |13.

The provision of the upper and lower parallel apertures |15 and |16 and the shape ofthe wheel truck |14 permits vertical adjustment of thewheels |18 relative to the thrust bearing member |65 and tubular housing |66 to any one of four desired positions. By removing the retaining bolt |13 and the bearing pin |1|, and re-inserting the latter in the upper apertures 15 instead of the lower apertures |16, the wheels |18 may be moved downward'relative to the rest of the wheel supporting structure from their/full line position of Fig. 8 to their first broken line position therebelow. By removing the pin |1| and turning the wheel truck |14 and wheels |18 through an angle of 180 degrees, re-insertion of the pin |1| in the apertures |15 will bring the wheels into their second broken line position, and insertion of the y pin |1| in the apertures |16 will bring the wheels into their lowermost broken line position of Fig. 8.

The rear surface of each of the tubular housings |66 (Figs. 8 and 9) is provided with an elongated vertical slot |83 which serves two functions: First, it provides clearance for the conduit |59 (or 16|) leading to the lower port |35 in the plug member |32 of the stationary cylinderk |3| during vertical movements of the wheel supporting structure l |5 relative thereto. Secondly, the slot |83, in conjunction with a bolt |84 which is screwed into a suitable aperture in a boss |85 on the lower part of the stationary housing H5, holds the wheel structure ||5 in line and prevents it from rotating about a vertical axis relative to the supporting structure 4. .The bolt |84 may be locked in any desired adjusted position by a nut |86. l i Diametrically opposed to the boss4 |85, each of the housings ||6 is provided with another boss |81 (Figs. 8 and 5) having a' threaded aperture extending therethrough. A bolt |86 is adapted to be screwed into rthis aperture, and is provided with an axial recess within which is housed a. coil spring |88 and a ball |9 the latter being urged against the outer surface of the tubular housing |66 by the spring. Adjustment of the bolt |88 determines the force exerted by'the spring |89 against the ball |9|'.

Adjacent its lower end anddiametrically opposed t the slot |83,'the tubular housing |66 is provided with a countersunk aperture |92 of such diameter that the ball |9| may Venter .but not pass through it. The aperture |92 is so positioned that, when the wheel supporting structure H is in its uppermost or retracted position, indicated in Fig. 8 by the uppermost broken line position of the wheels |18, the ball |9| will be forced into the aperture |92 by the spring |89 to resiliently lock the wheel supporting structure ||5 against accidental displacement from such retracted position. It will be readily understood that this locking mechanism may equally well be applied to the bracket 63 and sleeve 59, or the sleeves 59 and 62 of the swingingtype landing gear |3 of Figs. 1 to 4, if it is desired.

In order to operate the above described hydraulic landing gear of Figs. 5 to 10, the removable pump handle |48 is secured to the shaft |49, the valve handle |56 positioned to constrain ow of fluid from the pump into the upper part of the cylinders |3| through the conduit |54, or into the lower part of the cylinders through the conduit |55, and the handle |48 is oscillated a suillcient number of times to positively force the piston. |42 and piston rods |34 to the desired position, either downwardly or upwardly.

So long as the valve handle |56, or its valveV shaft operated thereby, remains in its set position', the piston rods |34, and consequently the wheel supporting structures ||5, will be maintained in set position, since the fluid in the system may not flow backwardly through the pump unit |46. If the valve handle |56 is moved to its neutral position of Fig'. 10, however, or to the position opposite to which it was originally set, vthe reactive forces against the pistons |42 may cause displacement of -the wheelsupporting structures from their set position. 'I'his will only occur, however, when the landing gear is in retracted position, and the locking mechanism |88- |92 will then prevent such accidental displacement.

It is thought that the invention and many of its attendant advantages will be understood from the foregoing description, and it will be apparent that various changes may be made in the form, construction and arrangement of the parts without departing from the spirit and scope of the invention or sacriclng all of itsmaterial advantages, the forms hereinbefore described bein merely preferred embodiments thereof. i

-I claim: y

1. In a tractor, trailer vehicle having cooperating fth wheel mechanisms on said tractor and said trailer including a king pin, arretractible landing gear mounted on said trailer, a double acting hydraulic ram automatically operable by said king pin in the coupling and uncoupling of said fifth wheel mechanisms, a second hydraulic ram operable by said first ram to raise and lower said landing gear, a iluid supply reservoir, and connections between said reservoir and said rams for transmitting movements oi said iirst ram to said second ram, including valve means for insuring a proper iluid supply at all times from said reservoir and for permitting the escape of any air entrained by said iiuid.

2. In a system for hydraulically transmitting the relative movement between two members to a. third member mounted on one oi said members, a flrst hydraulic ram mounted on one of said first two members for operation by the other oi.' said members in the relative movement therebetween, a second hydraulic ram interconnected between said ilrst ram supporting member and said third member for moving the latter relative thereto, a iluid supply reservoir, and connections between said reservoir and said rams for hydraulically transmitting movements of said ilrst ram to said second ram, including valve means for insuring the proper fluid supply at all times from said reservoir and for permitting the escape of any air entrained by said uid.

3. A landing gear for trailers, comprising a wheel supporting structure mounted for movement relative to the trailer and a hydraulic operating system for said wheel supporting structure, comprising a first ram mechanism, a second ram mechanism operatively associated with said wheel supporting structure for moving the latter between retracted and lowered positions, a iluid supply reservoir for insuring the proper amount of uid at all times, and connection between said reservoir and said ram mechanisms for hydraulically transmitting movements of said ilrst ram mechanism to said second ram mechanism, including valve means for controlling the supply of iiuid from said reservoir and for permitting the4 automatic escape of air entrained by said fluid from the system.

4. In a system for hydraulically transmitting the relative movement between tractor and trailer vehicles during coupling and uncoupling operations thereof to a landing gear mounted on the 

